EP4018112A1 - Convertisseur de couple hydrodynamique doté d'un embrayage de verrouillage de convertisseur - Google Patents

Convertisseur de couple hydrodynamique doté d'un embrayage de verrouillage de convertisseur

Info

Publication number
EP4018112A1
EP4018112A1 EP20746546.9A EP20746546A EP4018112A1 EP 4018112 A1 EP4018112 A1 EP 4018112A1 EP 20746546 A EP20746546 A EP 20746546A EP 4018112 A1 EP4018112 A1 EP 4018112A1
Authority
EP
European Patent Office
Prior art keywords
converter
hydrodynamic torque
torque converter
housing
turbine wheel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP20746546.9A
Other languages
German (de)
English (en)
Inventor
Toros GÜLLÜK
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP4018112A1 publication Critical patent/EP4018112A1/fr
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0205—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type two chamber system, i.e. without a separated, closed chamber specially adapted for actuating a lock-up clutch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
    • F16H2045/0231—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers arranged in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0247—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means having a turbine with hydrodynamic damping means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0263—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means the damper comprising a pendulum
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0284—Multiple disk type lock-up clutch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0294—Single disk type lock-up clutch, i.e. using a single disc engaged between friction members

Definitions

  • the invention relates to a hydrodynamic torque converter with a converter housing and a converter torus with a pump wheel, a turbine wheel hydrodynamically driven by the pump wheel by means of a converter fluid, a converter lock-up clutch switched between the pump wheel and the turbine wheel by means of pressurization of the converter fluid to bridge the hydrodynamic drive is arranged radially between an outer circumference of the wall lergephaseuses and the converter torus.
  • Hydrodynamic torque converters are used in motor vehicle drive trains as starting clutches with excessive torque.
  • a pump wheel connected to a converter housing transmits torque to the turbine wheel by means of a converter fluid, the converter fluid being supported on a stator while the vehicle is moving off, with the starting torque increasing.
  • the pump wheel and the turbine wheel are frictionally connected by means of a converter lockup clutch after the start-up process.
  • a hydrodynamic torque converter is known in which the converter lockup clutch is formed from an actuating piston that is integrally arranged on the turbine wheel.
  • the actuating piston engages over a torsional vibration damper and contains a friction lining, which is axially spaced from the turbine wheel and within a diameter of a converter torus composed of the pump wheel and turbine wheel and forms a frictional connection with a counter-friction surface arranged on the converter housing.
  • the converter lock-up clutch is dependent on in the converter housing adjusted pressure of the converter fluid acting on the actuating piston is actuated.
  • the section of the converter lock-up clutch arranged on the turbine wheel is designed as an axially displaceable actuating piston with a friction lining which, depending on the pressure of the converter fluid, has a counter-friction surface of the converter housing in Frictional engagement occurs.
  • the object of the invention is to develop a generic hydrodynamic torque converter.
  • the object of the invention is to propose a hydrodynamic torque converter with a further improved transmission capacity of the converter lock-up clutch.
  • the proposed hydrodynamic torque converter is used to transmit torque with the function of a starting clutch with excessive torque between a drive unit, for example an internal combustion engine or an internal combustion engine in conjunction with an electric machine and an automatic transmission of a drive train of a motor vehicle.
  • the torque converter contains a converter housing in which a converter torus with a predetermined outer diameter is housed.
  • the converter torus has an impeller with drive lamellae, which can be connected to the converter housing, for example by means of a friction clutch, or is integrated into the converter housing, and an axially opposing turbine wheel with lamellae hydrodynamically driven by the drive lamellae by means of a converter fluid contained in the converter housing, and one between the pump wheel and the turbine wheel arranged, by means of a freewheel on a gear-fixed connected converter neck supported stator.
  • a converter bridging clutch connected between the pump wheel and the turbine wheel by means of pressurizing the converter fluid is assigned.
  • the corresponding friction surfaces provided between the converter housing and the turbine wheel are arranged on a large diameter radially between an outer circumference of the converter housing and the wall lertorus.
  • the turbine wheel has at least one friction lamella, which can be axially preloaded between a pressurized annular piston that is axially displaceable in the converter housing and a converter housing section radially outside the converter torus.
  • the ring piston is sealed radially on the outside with respect to the converter housing and axially displaced and rotatably received on this.
  • a shoulder of a second, axially overlapping with a first housing shell of the converter housing can be tightly sealed with the first housing shell welded housing shell have an end profile that is interlocked with a complementary end profile of the annular piston.
  • the axial length of this profiling is dimensioned so that an axial travel of the annular piston is covered when the converter lock-up clutch is actuated.
  • a friction lining is arranged on the annular piston, which forms frictional engagement with a counter friction surface made of steel of the at least one friction plate.
  • this friction lining and the opposing friction surface preferably have a friction pairing that is tight for the converter fluid.
  • the frictional engagement between a counter-friction surface of the converter housing section or, in the case of several friction plates, a further friction plate takes place in each case by means of a friction pair consisting of a friction lining arranged on a friction plate and a counter-friction surface made of steel on the other side of the friction plate.
  • the friction linings can be designed as paper linings or sintered or pressed mixed linings.
  • heat is dissipated via the annular piston or via the friction plate.
  • the other frictional engagements can have grooves for better cooling, in particular grooves leading from the radial inside to the radial outside.
  • the friction engagement forming the frictional engagement with respect to the converter housing section can have grooves in order to displace excess converter fluid radially inward when the converter bridging clutch is closed.
  • one or more friction disks can be provided, which can be axially layered and rotatably hung in a wheel connected to the turbine, for example welded inner disk carrier.
  • the friction disks alternate axially with a corresponding number of friction disks, which are suspended in a rotationally test manner in an outer disk carrier connected to the converter housing.
  • Such a disk pack of alternately layered friction disks of the converter housing and the turbine wheel are axially biased by the annular piston against a converter housing section with a counter-friction surface radially outside the converter torus and within its installation space.
  • the outer disk carrier can be formed from a ring part with appropriate profiling such as circumferential toothing, which can be attached to the inside of the outer circumference of the converter housing, for example an axial approach of a housing shell with the pump wheel, for example welded.
  • the outer disk carrier can be shaped or embossed as a circumferential profile in the outer circumference of the converter housing, for example in the axial extension of the housing shell.
  • the hydrodynamic torque converter advantageously contains a torsional vibration damper, which is effectively arranged between the turbine wheel and an output hub with which the turbine wheel is also received, for example centered.
  • the input part of the torsional vibration damper is connected to the turbine wheel, for example welded, hooked in by means of straps and soldered or otherwise tightly and firmly connected to the blades of the turbine wheel.
  • the turbine wheel can be received directly on the output hub or connected to the output part of the torsional vibration damper.
  • the turning Vibration damper can be designed in several stages. For example, several sets of helical compression springs distributed over the circumference can be arranged on different diameters between the input part and the output part.
  • helical compression springs designed as arc springs can be received in a retaining shell distributed radially on the outside over the circumference. Radially inside, short helical compression springs can be distributed over the circumference between the input part and the output part.
  • the output part can, for example, form the retaining shell for the arc springs, while a flange part, which is connected to the turbine wheel and designed as an input part, engages in the retaining shell and acts on the arc springs on the input side.
  • a gear part can here form the inner disk carrier of the converter lockup clutch formed with several friction disks.
  • the retaining shell can be received on the turbine wheel, for example welded to it.
  • a flange part provided on the output part engages on the output side in the retaining shell to act on the arc springs on the output side.
  • a centrifugal pendulum can be provided in addition to the torsional vibration damper.
  • the centrifugal pendulum is added to the rotary vibration damper.
  • the centrifugal pendulum can be connected to the output part.
  • a pendulum mass carrier of the centrifugal force pendulum with pendulum masses arranged in a pendulum fashion on both sides and a side part for acting on radially inner helical compression springs can be formed in one piece.
  • FIG. 1 shows the upper part of a hydrodynamic torque converter arranged around an axis of rotation, in section
  • FIG. 2 shows the upper part of a torque converter arranged around an axis of rotation and modified compared to the torque converter of FIG. 1 with a disk pack in section,
  • FIG. 3 shows the upper part of a torque converter arranged around an axis of rotation and modified compared to the torque converter of FIG. 2 with a disk pack in section,
  • FIG. 5 shows the upper part of a torque converter arranged around an axis of rotation and modified compared to the torque converter of FIG. 4 with a disk pack in section.
  • FIG. 1 shows the upper part of the hydrodynamic torque converter 1, which is arranged so as to be rotatable about the axis of rotation d, in section.
  • the converter housing 2 is formed from the two housing shells 3, 4 which overlap each other axially radially on the outside and are tightly connected to one another.
  • the housing shell 3 contains the pump wheel 5 with drive lamellae distributed over the circumference.
  • the turbine wheel 6 is arranged with lamellae that are complementary to the drive lamellae of the pump wheel 5 and are attached to the turbine shell 7.
  • the stator 8 is arranged between the pump wheel 5 and the turbine wheel 6.
  • the pump wheel 5, the turbine wheel 6 and the stator 8 form the converter torus 9.
  • the wall lerb Wegungskupplung 10 Radially outside the converter torus 9 and in its axial installation space, the wall lerb Wegungskupplung 10 is arranged, which contains the annular piston 11, the friction plate 12 and the counter friction surface 13 on the converter housing section 14 as functional components.
  • the annular piston 11 is held in a rotationally fixed manner by means of the profiling 15 of the housing shell 4 and is received in a sealed manner on the converter housing 2 and with respect to it by means of the sealing ring 16.
  • the annular piston 11 By increasing the pressure in the chamber 17 of the converter housing 2 filled with converter fluid, the annular piston 11 is axially displaced and biases the Reibla melle 12 against the counter friction surface 13 with the formation of frictional engagement.
  • the friction plate 12 is formed in one piece from the turbine shell 7 by radially expanding the latter.
  • the friction plate 12 contains the opposite friction surface 13 facing the friction lining 18.
  • the frictional engagement between the annular piston 11 and the friction plate 12 is formed by means of the friction lining 19 arranged on the annular piston 11 and a steel surface of the friction plate 12.
  • the friction lining 19 has no grooves and thus forms a tight friction surface to the friction plate 12, while the friction lining 18 forms grooves 18a from radially inside to radially outward, so that when the converter lockup clutch 10 closes, superfluous converter fluid is displaced radially inward.
  • the hydrodynamic torque converter 1 contains the torsional vibration damper 20 within the chamber 17, the input part 21 of which is connected to the turbine wheel 6 and the output part 22 of which forms the output hub 23 with the internal toothing 24, which is rotatably connected, for example, by means of a transmission input shaft of a transmission.
  • the torsional vibration damper 20 is designed in two stages and has for this purpose helical compression springs 25 arranged as arc springs distributed radially outward over the circumference and short helical compression springs 26 arranged radially inwardly distributed over the circumference.
  • the helical compression springs 25 are supported in the retaining shell 27 against the effects of centrifugal force and are hit on the output side by this beiller.
  • the input-side loading takes place by means of the flange part 28, which is designed as an input part 21 and which is welded to the turbine shell 7.
  • the helical compression springs 25 are arranged radially outside of the converter torus 9 in the chamber 17 to save space.
  • the helical compression springs 26 are arranged to save space radially within the maximum axial extent of the turbine wheel 6 and received in window-shaped recesses of the side parts 29, 30 and the output flange 31 arranged between them and applied to the input and output sides.
  • the side parts 29, 30 are connected to one another axially spaced apart by means of the spacer bolts 32 and support the helical compression springs 26 by means of axially raised window wings 33.
  • the connection of the damper stages with the helical compression springs 25, 26 takes place by means of the retaining shell 27, which forms the side part 30 facing the turbine shell 7.
  • the output flange 31 is integrally connected to the output hub 23.
  • the turbine wheel 6 is by means of the turbine flange 34, which is connected to the turbine shell 7 by means of the rivet 35, centered on a shaft, not shown, such as the transmission input shaft of a transmission.
  • the torsional vibration damper 20 is effective when the converter lockup clutch 10 between the converter housing 2 and the output hub 23 is closed.
  • the torsional vibration damper 20 is effective as a so-called turbine damper by the torque transmitted from the pump wheel 5 to the turbine wheel 6 via the torsional vibration damper 20 to the output hub 23.
  • FIG. 2 shows the upper part of the hydrodynamic torque converter 101, which is similar to the hydrodynamic torque converter 1 and is arranged to be rotatable about the axis of rotation d, in section.
  • the hydrodynamic torque converter 101 has the converter bridging clutch 110 with the friction disk 136 in addition to the friction disk 112 formed from the turbine shell 107 of the turbine wheel 106.
  • the friction lamella 136 is suspended in a rotationally fixed manner by means of an inner profile in the input part 121 of the torsional vibration damper 120 which acts as an inner lamella carrier 137.
  • the friction disk 140 is rotatably attached to the outer disk carrier 139 of the housing shell 103 of the converter housing 102.
  • the annular piston 111, the friction plate 136, the friction plate 140, the friction plate 112 and the counter-friction surface 113 of the converter housing section 114 form the layering of the disk set 138 the annular piston 111 from the side facing away from friction linings 118, 141, 142, so that a friction pairing friction lining / steel is formed in each case.
  • FIG. 3 shows the upper part of the hydrodynamic torque converter 201, which is arranged around the axis of rotation d and is similar to the hydrodynamic torque converter 101 of FIG. 2, in section.
  • the hydrodynamic torque converter 201 has the Torque converter lockup clutch 210 with the disk pack 238, the inner lamellar carrier 237 of which is formed separately from the flange part 228 of the input part 221 of the torsional vibration damper 220.
  • the inner disk carrier 237 and the flange part 228 are each welded to the turbine shell 207 of the turbine wheel 206 independently of one another.
  • the inner disk carrier 237 also has the radial support weld 243 in order to avoid a deviation of the inner disk carrier 237 after ra dial inside.
  • FIG. 4 shows the upper part of the hydrodynamic torque converter 301 arranged around the axis of rotation d, which is provided with the centrifugal pendulum 344 as a modification to the hydrodynamic torque converters 1, 101, 201 of FIGS.
  • the centrifugal pendulum 344 is connected to the output-side part of the torsional vibration damper 320.
  • the Pendelmas scht 345 is formed in one piece with the side part 329.
  • the pendulum masses 346 received on both sides by means of self-aligning bearings, not shown, in the centrifugal force field of the torque converter 301 rotating about the axis of rotation d pendulously on the pendulum mass carrier 345 are received at the radial height of the helical compression springs 325.
  • the retaining shell 327 is designed as an input part 321 on the aisle side and is welded to the turbine shell 307 of the turbine wheel 306.
  • FIG. 5 shows the upper part of the hydrodynamic torque converter 401, which is arranged so as to be rotatable about the axis of rotation d, in section.
  • the outer disk carrier 439 is formed in one piece from the housing shell 403 of the converter housing 402.
  • indentations 448 forming the inner profile of the outer disk carrier 439 are provided in the axial extension 447 of the housing shell 403 distributed over the circumference in a radially inward direction. It goes without saying that the outer disk carriers of the torque converters 101, 201, 301 of FIGS. 2 to 4 can also contain such formations 448.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

La présente invention concerne un convertisseur de couple hydrodynamique (1) doté d'un logement de convertisseur (2) et d'un tore de convertisseur (9) avec une roue de pompe (5), et une roue de turbine (6) qui est entraînée de manière hydrodynamique par la roue de pompe (5) au moyen d'un fluide de convertisseur. Pour le pontage de l'entraînement hydrodynamique, un embrayage de verrouillage de convertisseur (10) qui est raccordé entre la roue de pompe (5) et la roue de turbine (6) par une charge de pression du fluide de convertisseur est disposé radialement entre une circonférence externe du logement de convertisseur (2) et le tore de convertisseur (9). Afin de fournir un embrayage de verrouillage de convertisseur (10) ayant une capacité de transmission accrue, la roue de turbine (6) est associée à au moins un disque de friction (12) qui peut être précontraint axialement entre un piston annulaire sollicité par pression (11), qui est accroché de manière mobile axialement dans le logement de convertisseur (2), et une surface de friction complémentaire (13) d'une section logement de convertisseur (14) radialement à l'extérieur du tore de convertisseur (9).
EP20746546.9A 2019-08-23 2020-07-02 Convertisseur de couple hydrodynamique doté d'un embrayage de verrouillage de convertisseur Pending EP4018112A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019122692.9A DE102019122692B4 (de) 2019-08-23 2019-08-23 Hydrodynamischer Drehmomentwandler mit Wandlerüberbrückungskupplung
PCT/DE2020/100579 WO2021037298A1 (fr) 2019-08-23 2020-07-02 Convertisseur de couple hydrodynamique doté d'un embrayage de verrouillage de convertisseur

Publications (1)

Publication Number Publication Date
EP4018112A1 true EP4018112A1 (fr) 2022-06-29

Family

ID=71833091

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20746546.9A Pending EP4018112A1 (fr) 2019-08-23 2020-07-02 Convertisseur de couple hydrodynamique doté d'un embrayage de verrouillage de convertisseur

Country Status (5)

Country Link
US (1) US11808335B2 (fr)
EP (1) EP4018112A1 (fr)
CN (1) CN114270076A (fr)
DE (1) DE102019122692B4 (fr)
WO (1) WO2021037298A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11781618B2 (en) * 2016-09-16 2023-10-10 Aisin Aw Industries Co., Ltd Damper device

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2943516A (en) * 1957-07-05 1960-07-05 Gen Motors Corp Transmission
US5400884A (en) * 1992-05-14 1995-03-28 Kabushiki Kaisha Daikin Seisakusho Torque convertor
US6296019B1 (en) * 1997-08-26 2001-10-02 Luk Getriebe-Systeme Gmbh Pressure medium system
CN104755813B (zh) 2012-10-04 2017-07-11 舍弗勒技术股份两合公司 涡轮活塞推进路径
CN106062424B (zh) * 2013-07-23 2019-06-18 舍弗勒技术股份两合公司 包括预载的可轴向移动的涡轮的弹性元件在内的转矩变换器
US20150152951A1 (en) * 2013-12-03 2015-06-04 Schaeffler Technologies Gmbh & Co. Kg Torque converter with integrated triple plate lock-up clutch
US9297448B1 (en) * 2014-10-23 2016-03-29 Valeo Embrayages Hydrokinetic torque coupling device having turbine-piston lockup clutch, and related methods
US9441718B2 (en) * 2014-10-23 2016-09-13 Valeo Embrayages Hydrokinetic torque coupling device having turbine-piston lockup clutch, and related methods
JP5925867B1 (ja) * 2014-11-25 2016-05-25 株式会社エクセディ 流体継手
DE102015215902A1 (de) * 2015-08-20 2017-02-23 Schaeffler Technologies AG & Co. KG Fliehkraftpendel und hydrodynamischer Drehmomentwandler mit Fliehkraftpendel
DE102017102730A1 (de) * 2017-02-13 2018-08-16 Schaeffler Technologies AG & Co. KG Hydrodynamischer Drehmomentwandler mit drehzahladaptivem Drehschwingungstilger
US10180182B2 (en) * 2017-03-02 2019-01-15 Valeo Embrayages Turbine-piston for hydrokinetic torque converter and method of operation
US10260611B2 (en) * 2017-03-31 2019-04-16 Valeo Embrayages Hydrokinetic torque coupling device having turbine-piston lockup clutch, and related methods

Also Published As

Publication number Publication date
WO2021037298A1 (fr) 2021-03-04
US20220333672A1 (en) 2022-10-20
DE102019122692B4 (de) 2021-06-10
CN114270076A (zh) 2022-04-01
US11808335B2 (en) 2023-11-07
DE102019122692A1 (de) 2021-02-25

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